WO1985002824A1 - Vehicule de travail a courroie a entrainement par friction - Google Patents

Vehicule de travail a courroie a entrainement par friction Download PDF

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Publication number
WO1985002824A1
WO1985002824A1 PCT/US1984/000560 US8400560W WO8502824A1 WO 1985002824 A1 WO1985002824 A1 WO 1985002824A1 US 8400560 W US8400560 W US 8400560W WO 8502824 A1 WO8502824 A1 WO 8502824A1
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WO
WIPO (PCT)
Prior art keywords
belt
wheel
pair
vehicle
laying vehicle
Prior art date
Application number
PCT/US1984/000560
Other languages
English (en)
Inventor
Charles E. Grawey
Robert J. Grob
Cullen P. Hart
Original Assignee
Caterpillar Tractor Co.
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Family has litigation
First worldwide family litigation filed litigation Critical https://patents.darts-ip.com/?family=24250112&utm_source=google_patent&utm_medium=platform_link&utm_campaign=public_patent_search&patent=WO1985002824(A1) "Global patent litigation dataset” by Darts-ip is licensed under a Creative Commons Attribution 4.0 International License.
Application filed by Caterpillar Tractor Co. filed Critical Caterpillar Tractor Co.
Priority to DE8484901712T priority Critical patent/DE3479019D1/de
Priority to BR8407219A priority patent/BR8407219A/pt
Priority to CA000468799A priority patent/CA1222271A/fr
Publication of WO1985002824A1 publication Critical patent/WO1985002824A1/fr

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B62—LAND VEHICLES FOR TRAVELLING OTHERWISE THAN ON RAILS
    • B62D—MOTOR VEHICLES; TRAILERS
    • B62D55/00—Endless track vehicles
    • B62D55/08—Endless track units; Parts thereof
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B62—LAND VEHICLES FOR TRAVELLING OTHERWISE THAN ON RAILS
    • B62D—MOTOR VEHICLES; TRAILERS
    • B62D55/00—Endless track vehicles
    • B62D55/06—Endless track vehicles with tracks without ground wheels
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B62—LAND VEHICLES FOR TRAVELLING OTHERWISE THAN ON RAILS
    • B62D—MOTOR VEHICLES; TRAILERS
    • B62D55/00—Endless track vehicles
    • B62D55/08—Endless track units; Parts thereof
    • B62D55/18—Tracks
    • B62D55/24—Tracks of continuously flexible type, e.g. rubber belts
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B62—LAND VEHICLES FOR TRAVELLING OTHERWISE THAN ON RAILS
    • B62D—MOTOR VEHICLES; TRAILERS
    • B62D55/00—Endless track vehicles
    • B62D55/08—Endless track units; Parts thereof
    • B62D55/30—Track-tensioning means

Definitions

  • This invention relates to crawler-type vehicles, tractors or equipment having tracks over wheels for providing both ground support and tractive effort, and more particularly, to a system for frictionally transmitting motive force through an interface between a wheel and a ground engaging belt.
  • the objective of this invention to provide a workable solution to the problems by taking into account that such vehicle's undercarriage, to be truly useful, should be roadable, provide high traction and low ground compression, and minimally disturb the underlying terrain, as well as operate in the heavy-duty working mode and provide a smooth ride for the operator in most soil conditions and topography from level land to steep inclinations while performing useful work without breaking the belts, losing drive capability between engaged wheels and belts, or disengaging the belts from the wheels.
  • the present invention generally includes a chassis, a pair of longitudinally spaced wheels arranged on each lateral side of the chassis in supporting relation thereto, an endless belt having an elastomeric exterior surface and being highly tensioned to provide frictional coupling between an interior surface thereof and the outer periphery of at least one wheel of each pair , and guide apparatus for maintaining lateral registry between each belt and the associated wheels.
  • the belt tension is regulated by a tensioning apparatus which maintains the frictional coupling, accommodates debris ingestion between the belt and wheels without damaging either, and augments the guide apparatus in maintaining lateral belt to wheel registry.
  • the belts are longitudinally reinforced to permit their high degree of tensioning and are laterally and transversely reinforced to resist movement in those directions and further augment the guide apparatus in retaining lateral registration.
  • Fig. 1 is a side elevation view of the work vehicle
  • Fig. 2 is a front elevation view of the work vehicle illustrated in Fig. 1;
  • Fig. 3 is a plan view taken along line III-III of Fig. 1;
  • Figs. 4 and 5 are respective sectional views of a preferred and an alternate belt construction
  • Figs. 6, 7, and 8 are respective partial sectional views of a preferred, first alternate, and second alternate drive wheel structure
  • Fig. 9 is a partial sectional view of a preferred idler wheel structure
  • Fig. 10 is a partial sectional view taken along line X-X of Fig. 2;
  • Figs. 11A and 11B are diagrammatic views of belt portions respectively defining "lateral” and “transverse” flexibility
  • Figs. 12A, 12B, and 12C are diagrammatic, partial sectional views of an engaged driver wheel-belt structure subjected to varying lateral loads;
  • Fig. 13 is a graphical representation of belt/wheel structure lateral load carrying as a function of deformation thereof;
  • Figs. 14A, 14B, 14C, 14D, 14 ⁇ , and 14F are diagrammatic representations of the relative operational configurations of a bias tire/belt and a rigid or cushioned wheel/belt and wear characteristics exhibited thereby;
  • Fig. 15 is a graphical representation contrasting the present invention's mean power efficiencies with 4-wheel drive vehicle's mean power efficiencies for different soil/soil conditions;
  • Fig. 16 is a graphical representation of the pull/weight ratio as a function of the propulsion system's slip percentage for the present invention and a 4-wheel drive vehicle.
  • FIG. 1 illustrates an exemplary belt laying work vehicle 10 having a chassis 12 with a longitudinal axis 14 and a propulsion system 16 which reside-s generally beneath and in supporting relation to a frame 18 which, together with an operator 's station 20 and an engine 22, constitutes the chassis 12.
  • a rearwardly protruding drawbar 23 is joined to the frame 18 and constitutes an attachment structure to which draft loads may be connected.
  • OMPI principles inherent in such exemplary structure are applicable to heavy-duty propulsion systems for other vehicles whether such vehicles are used for hauling, pushing, or pulling large loads.
  • the illustrated draft work vehicle 10 was chosen as the exemplary apparatus since it has been actually reduced to practice and tested in a wide range of soil conditions, topographies, and loading characteristics.
  • the propulsion system 16 includes two pairs of longitudinally spaced apart wheel structures 24,26 which are arranged on opposite lateral sides 28,30 of the vehicle chassis 12 and which have respective radially outwardly facing peripheral surfaces 32,34, a pair of endless, substantially inextensible belts 36 each having an interior 38 and an exterior 40 surface which are respectively engaged with the wheel's outer peripheral surfaces 32,34 and the underlying terrain, and a roller support system 42 which is joined to the frame 18 on each lateral side of the chassis 12 and which is engageable with each belt's interior surface 38 longitudinally between the separated wheel structures 24,26 of each pair.
  • the endless characteristic of the belt 36 means that the belt is continuous and has no connection joint is).
  • the propulsion system 16 has substantially identical components on each lateral side 28,30 of the chassis 12, further reference will only be made to the set of components on the .side 28.
  • At least one of the wheel structures on each lateral side- of the chassis 12 constitutes a driver wheel structure 44 which frictionally transmits power to the belt 36 from the chassis-mounted engine 22.
  • the wheel structures 24,26 on each side are laterally aligned and have respective circumferential guide channels 46,48 which are each laterally bounded by positioning surfaces
  • OMPI 50,52 are adapted for receiving belt-resident guide structures.
  • the other wheel structure on each side constitutes an idler wheel structure 54 which helps to support the vehicle chassis 12, cooperates with the driver 44 to provide a path 56 along which the belt 36 can be driven, and, in the illustrated case, provides a measure of recoil capability.
  • the front wheel structure 26 could also constitute a driver.
  • the rear wheel structure 24 of the illustrated draft vehicle constitutes the driver wheel structure 44 and the front wheel structure 26 constitutes the idler wheel structure 54.
  • the rear 24 and front 26 wheel structures are respectively mounted on laterally protruding axles 58,60 so as to rotate about respective axes .62,64 during vehicle movement.
  • the driver wheel structure 44 has arcuately spaced, laterally extending grooves 68 distributed in its outer peripheral surface 32. Each pair of adjacent grooves 68 defines an intermediate protuberance 70 having arcuately bounding walls or edges 72,74 of desired radial height 76 and an outwardly facing drive portion 77 of predetermined arcuate length 78 which constitutes the outer peripheral surface 32. "Leading” and “trailing” as used herein refers to the relative positioning of like elements during movement thereof.
  • grooves 68 are arranged in the driver 44 at substantially 90° to the chassis' longitudinal axis and have radially oriented bounding walls 72,74, it is to be understood that the grooves 68 could be formed in the belt's interior surface 38 and that other angular arrangements of the grooves 68 and other wall orientations are operationally acceptable for purposes of the present invention.
  • the "grooved" configuration thus provides a substantial contribution in maintaining the driving relationship regardless of the environment.
  • the front wheel structure 26 has a smooth outer peripheral surface 34 about which the belt 36 is entrained and engaged.
  • the front wheel structure 26 in the illustrated embodiment constitutes an idler 54, maintaining a friction couple between it and the entraining belt's interior surface 38 is unnecessary.
  • the interior surfaces 38 of the endless, inextensible belts 36 illustrated in Figs. 1, 2, and 3 constitute elastomer and are smooth to facilitate frictional .engagement thereof with the associated driver 44 while the exterior surfaces 40 have elastomeric cleats 80 protruding therefrom for penetrating the underlying ground and enhancing the belt's tractive capability.
  • the elastomeric character of the cleats 80 permits the illustrated vehicle 10 to travel on improved road surfaces without damaging same.
  • each belt 36 has an ultimate elongation of less than 5% to permit tensioning thereof with reasonable movements of tensioning apparatus and must be capable of sustaining tension loads of approximately 17,000 Newtons per lateral centimeter of belt width to provide the driving friction force typically transmitted by heavy-duty vehicles weighing in excess of about 4,500 Kilograms.
  • each belt 36 has a guide structure 82 which is receivable in the wheels' guide channels 46,48 for maintaining lateral registry between each belt 36 and its entrained wheel structures 24,26.
  • Each guide structure 82 includes alignment members 84 which are longitudinally separated, by way of example, by about 5.5 centimeters, preferably extend inwardly from the lateral center of the associated belt's interior surface 38, and have a high modulus of elasticity.
  • the rear 24 and front 26 wheel structures are relatively rigid in the lateral direction as compared to radial tires so as to promote belt guiding thereon for heavy-duty vehicle operation on side slopes or in other circumstances where the vehicle is subjected to high lateral loading. Due to the character of the exemplary draft vehicle 10 and for reasons to be discussed later relating to wear, greater lateral rigidity of the driver wheel structure 44 is required than of the idler wheel structure 54.
  • the preferred driver wheel structure 44 constitutes a cushi-oned wheel structure 85 which is illustrated in Fig. 6, and includes a circular rigid metal drum 86 having a solid layer 90 of elastomer which is radially thin relative to the drum's diameter and which is bonded to the drum's outer periphery 92.
  • the elastomer layer's radial thickness is about 5 centimeters and the drum's radius is about 51 centimeters.
  • the circumferential guiding channel 46 is arranged about the cushioned wheel structure 85 generally along its mid-circumferential plane 93 to expose opposed inner edges 94 of the elastomeric layer 90 and opposed inner margins 95 of the drum 86.
  • the guiding channel 46 is defined by the laterally opposed positioning surfaces 50,52, each of which includes a base portion 96 and an inner portion 98 which, by way of example, have respective angles of inclination 97 of approximately 90 and 106 .
  • the base portions 96 constitute the inner edges 94 of the elastomeric layer 90 and the inner portions 98 constitute the inner margins 95 of the drums 86.
  • Such inner portions 98 preferably converge in a radially inward direction.
  • a rigid wheel structure 100 which includes a completely rigid circular drum 86 as illustrated in Fig. 7. Friction enhancing grooves 68 in the rigid wheel structure's outer periphery provide the same material expulsion capability as do the grooves 68 in the elastomeric layer 90.
  • the cushioned driver wheel structure's elastomeric layer 90 cooperates with the belt's interior elastomeric surface 38 to envelop in a non-penetration mode any hard, non-flowable elements such as stones which become sandwiched between the wheel structures 24,26 and entrained belt 36.
  • the rigid driver wheel structure 100 also includes a circumferential guiding channel 46 laterally defined by positioning surfaces 50,52.
  • the completely rigid wheel structure 100 requires additional elastomeric material on the interior of a mating belt structure 36 which is suitable for use with the cushioned wheel structure 85 so as to provide the
  • Fig. 8 illustrates another alternative driver wheel structure 44 which constitutes a pneumatic wheel structure 102 having a pair of laterally separated pneumatic wheels 104,106 which respectively include rigid rims 108,110 and inflatable, bias belted carcasses 112,114 mounted thereon.
  • the bias belted carcasses 112,114 have laterally facing adjacent sidewalls 116,118 which are substantially parallel and preferably each have an angle of inclination 97 of 90 relative to the outer peripheral surface 32 thereof.
  • the sidewalls 116,118 respectively include positioning surfaces 50,52 which define the circumferential guide channel 46.
  • the sidewalls 116,118 of the carcasses 112,114 are thicker and more planar to respectively provide greater lateral rigidity and better positioning surfaces 50,52 for engagement with the guide structure 82 with minimum surface area.
  • Radial tire carcasses have insufficient rigidity in the lateral direction to provide the guiding required in all heavy-duty applications but the bias carcasses 112,114 will, in certain heavy-duty applications, such as motor grader vehicles, provide the requisite lateral stiffness.
  • the lateral stiffness of the driver wheels 44 is an important factor in maintaining lateral registry of the belt 36 and wheels 24,26.
  • the outer periphery 32 of the alternate pneumatic driver wheel structure 102 constitutes circumferentially alternating friction enhancing grooves 68 and protuberances 70 whose structure is the same as that shown for the driver wheel structures 44 illustrated in Figs. 6 and 7.
  • Both the cushioned 85 and rigid 100 driver wheel structures are preferred over the pneumatic carcass driver wheel structure 102 for applications in which pantagraphing and/or relative motion between the wheel driver structure 44 and belt 36 cannot be tolerated and still provide reasonable wear.
  • bias tires, when under load also exhibit a phenomenon of tracing out a footprint for one revolution thereof which is shorter by approximately 2%-3% than is the circumference around such tire's outer periphery when unloaded.
  • Such circumferential changing phenomenon causes relative motion between each belt's interior surface 38 and the protuberance's drive portions 77.
  • Such motion results in wear of the leading edge 72 (for forward vehicle motion) of the protuberances 70 and thus reduces the arcuate length 78 of their drive portions 77.
  • the practical effect of such wearing substantially reduces the wiping action of the protuberances 70 on the interior surface 38 of the belt 36 which, in turn, reduces the friction coupling between the drive wheel structure 44 and the belt 36 ' when they are operated in mud or other adverse, friction coefficient reducing environments.
  • Such relative bias wheel-to-belt motion during frictional engagement is illustrated in Fig.
  • FIG. 14A where, for purposes of illustration, only one lateral groove 68 and associated protuberance's leading edge 72 are illustrated at the left side of Fig. 14A with the leading edge 72 being in circumferential alignment with a belt mark arrow 120 which marks the matching position of the belt 36.
  • the right side of Fig. 14A illustrates the relative positioning of the belt mark 120 and the protuberances' leading edge 72 after rotation of the bias wheel in the indicated direction.
  • the belt marker 120 moves a further linear distance than did the protuberances' leading edge 72 so as to demonstrate the relative movement therebetween.
  • Fig. 14B illustrates the principle that when such bias wheel is rotated under load for one revolution, it moves a linear distance A which is less than the bias wheel's circumference B when unloaded.
  • Fig. 14C The resulting wear of the protuberance's leading edge 72 is respectively shown in Fig. 14C.
  • Figs. 14D and 14E illustrate the lack of relative movement between an entraining belt 36 and a cushioned 85 or rigid 100 wheel structure as respectively shown in Figs. 6 and 7.
  • the rigid 100 or cushioned wheel 85 when rotated one revolution under load, traverses a linear distance C, as diagrammatically illustrated in Fig. 14E, which is substantially equal to its unloaded circumference B.
  • No relative movement between the driver's outer periphery 32 and the entraining belt 36 occurs during driver rotation as is sequentially illustrated in Fig. 14D. Accordingly, the leading edge 72 of the single illustrated protuberance 70 exhibits little wear, retains the shape illustrated in Fig.
  • Fig. 9 illustrates the preferred embodiment of the idler wheel structure 54 and constitutes a pair of inflatable pneumatic wheels 104,106 which are similar to those shown in Fig. 8, but lack the lateral, friction enhancing grooves.
  • r OT.*PI wheels 104,106 is arranged along the wheel structure's mid circumferential plane 107 and is bounded and defined by the adjacent, laterally facing positioning surfaces 50,52 which cooperate to provide belt-to-wheel guiding.
  • the work vehicle 10 illustrated in Fig. 1 is primarily intended for agricultural use and thus requires a limited but finite recoil capacity for cases where debris of a specified size may intrude between either of the wheel structures 24,26 and the belt 36.
  • the pneumatic idler wheel structure 54 due to its ability to elastically deform, inherently provides the degree of recoil necessary to accommodate debris normally encountered in most agricultural applications while continuing to function and without overstressing the belt, wheels, or support structure for the wheels. Such recoil capability is a contributing factor in non-destructably accommodating debris intrusion.
  • Figs. 4 and 5 respectively illustrate the presently preferred belt structure- 122 and an alternative belt structure 124.
  • the preferred belt structure 122 includes an elastomeric interior surface 38, an elastomeric exterior surface 40, and a pair of lateral sides 126,128 which respectively engage the wheel structures' outer peripheries 32,34, the underlying terrain, and bound the interior 38 and exterior 40 surfaces.
  • the preferred belt 122 has a body portion 130 which is defined by the interior 38 and exterior 40 surfaces and by the lateral, edges 126,128 and has a central plane 132.
  • the guide structure 82 joined to and protruding interiorly from the belt's interior surface 38 is receivable in the wheels' guiding channels 46,48 to maintain lateral registry therewith.
  • the longitudinally separated alignment members 84 each have a pair of opposed, generally laterally facing locating surfaces 134 and a tip surface 136.
  • Each locating surface 134 has a base portion 138 and an inner portion 140 which have respective exemplary angles of inclination 97 of approximately 94° and 110° relative to the laterally adjacent portion of the interior surface 38.
  • the locating surfaces' base portions 138 are radially co-extensive with the guide channel's base portions 96.
  • the height of the base 138 and inner 140 portions perpendicular to the interior surface 38 are about 5 and 10.2 centimeters, respectively.
  • Each alignment member 84 ' has, by way of example, a lateral width 141 of about 11.2 centimeters and a longitudinal length of about 15.2 centimeters.
  • the cleats 80 are attached to the exterior surface 40 of the belt and extend exteriorly therefrom.
  • At least one inextensible reinforcing filament 142 is wrapped longitudinally in the body portion 130 from one lateral side 126 thereof to the other lateral side 128 such that when the belt 122 is installed on the wheel structures 24,26, each circumferential wrap or turn 143 of the filament 142 is substantially parallel to the chassis' longitudinal axis 14.
  • the reinforcing filament is interiorly disposed within the body portion 130 and a pair of breaker plies 144,146, well-known in the art, are arranged in the body portion between the central plane 132 and the reinforcing filame.nt 142.
  • the breaker ply 144 adjacent the reinforcing filament is laterally more narrow than is the lateral extent of the filament wraps 143.
  • the breaker ply 146 disposed adjacent the central plane 132 is, in turn, laterally more narrow than the other breaker ply 144.
  • Each breaker ply 144,146 has stiffening fibers therein which are preferably arranged at 90 to the stiffening fibers in the adjacent breaker ply 144,146 and, in the installed position of the belt on ' the vehicle, are preferably oriented at 45° relative to the chassis' longitudinal axis 14.
  • a plurality of longitudinally separated, laterally extending reinforcing elements 148 are arranged in the body portion 130 on the opposite side of the central plane 132 from the reinforcing filament 142 and breaker plies 144,146.
  • the reinforcing filament 142 provides the belt 36 with its longitudinally inextensible yet flexible character which is necessary to resist undesired stretching of the belt 36 when it is subjected to the tension force necessary to frictionally couple it to the entrained driver wheel structure 44.
  • Such longitudinal reinforcement allows, however, sufficient belt flexibility to readily conform to the outer peripheries 32,34 of the wheel structures 24,26 without diverting undue amounts of power from the vehicle's engine 22 for longitudinally conforming the belt to the wheel structure's outer peripheries.
  • the lateral belt stiffness resists "snaking" as illustrated in Fig._llA and cooperates with the wheel structures 24,26 in maintaining lateral registry therewith by resisting side loads imposed by the vehicle's chassis.
  • the transverse stiffness provided by the lateral reinforcing elements 148 resists transversely imposed forces as illustrated in Fig.
  • 11B tends to promote the correct orientation of the belts' guide structure 82 for suitable reception in the guide channels 46,48, and contributes to maintaining the lateral registry between the belt 122 and wheel structures 24,26. Without such transverse stiffness, the belts 36 could assume the configuration illustrated in 11B and thus promote disengagement of the guide structure 82 from its guide channels 46,48 and, thus, disengagement of the belt 36 from the associated wheel structures.
  • An alternate belt structure 124 illustrated in Fig. 5, has an interior surface 38, an exterior surface 40, and opposed lateral edges 126,128 which respectively engage the wheel structures' outer peripheries 32,34, the underlying terrain, and laterally bound the interior 38 and exterior 40 surfaces.
  • the alternate belt structure 124 has a body portion 130 which is defined by the interior 38 and exterior 40 surfaces and the lateral edges 126,128 and has a central plane 132.
  • At least one reinforcing filament 142 similar to that of Fig. 4 is wrapped in the body portion 130 in a manner and location substantially identical to that of Fig. 4.
  • Fig. 4 illustrates a partial cutaway view of a portion of the propulsion system 16.
  • the center portion of the top belt run has been removed to expose the cooperative arrangement of the belt 36 and entrained wheel structures 24,26.
  • the front 26 and rear 24 wheel structures have respective mid circumferential planes 107,-93 which are preferably aligned along a common longitudinal path 150 which is parallel to the chassis' longitudinal axis 14.
  • the circumferential guiding channels 46,48 on the rear and front wheel structures lie along the path 150 so as to promote entry therein of the belt's guide structure 82.
  • the roller support system 42 distributes a portion of the weight and load imposed on the vehicle frame 18 to the belt's interior surface 38 longitudinally between the entrained wheel structures 24,26.
  • the roller support system 42 includes a mounting structure 152 which is pivotally connected to the frame 18 about a mounting axis 154, a leading 156 and a trailing 158 support arm connected to the mounting structure 152 and adapted to rotate about the mounting axis 154, a leading 160 and a trailing 162 connection structure which are respectively pivotally mounted on the leading 156 and trailing 158 support arms, two pair of roller structures 164,165 which are rigid in all directions and which are respectively rotatably mounted on the connection structures 160,162, and a force reaction structure 166 ' for biasing either support arm 156,158 increasingly toward the belt's interior surface 38 in response to the belt's interior surface 38 being increasingly biased toward the other support arm 156,158.
  • the biasing structure 166 includes a force transfer member 168 which is preferably pivot
  • Each roller structure 164 constitutes a pair of laterally separated roller elements 172 which are rollingly engaged with the belt's interior surface 38 on the lower belt run.
  • the separation distance between laterally adjacent roller elements 172 constitutes a guide slot 174 which is laterally aligned with the associated circumferential guide channels 46,48.
  • the belts' guide structures 82 longitudinally traverse the guide path formed by the wheel structures' circumferential guide channels 46,48 and the roller structures' guide slots 174.
  • Frictional coupling of the drive wheel 44 structure and entraining belt 36 requires biasing the belt into engagement with the driver wheel structure 44 with a normal force which, when multiplied by the coefficient of friction therebetween, is at least as great as the force which the engine 22 can exert on the ground through the belt 36 if a positive drive system was provided.
  • Each belt 36 is tensioned by separating the • longitudinally distal portions of the cooperating front 24 and rear 26 wheel structures. Common means for separating such longitudinally distal wheel structure portions include inflating the pneumatic carcasses 112,114 of the entrained wheel structures 24,26 and biasing the cooperating wheel structures 24,26 longitudinally apart either through wheel
  • the front wheels' pneumatic carcasses 112,114 can provide such recoil as well as tensioning the belts 36.
  • a recoil/tensioning apparatus 176 was separately provided and is shown in Fig. 10.
  • the front axle 60 of the exemplary work vehicle 10 is pivotally mounted on the frame 18 through a sliding spherical bearing 178 about a pivot pin 180 which defines a longitudinal pivot axis 182 which is parallel to the chassis' longitudinal axis 14.
  • the front axle 60 includes a frame mounted base portion 184 and two extension portions 186 which are each pivotally mounted at an intermediate region thereof to the base portion 184 about an adjustment pin 188.
  • Each axle extension portion 186 has a laterally outwardly protruding wheel mounting region 190 on which a front wheel structure 26 is mounted and an adjustment region 192 which protrudes inwardly and is connected to a "toe in - toe out" apparatus 194 for adjusting the orientation of the front wheel structures' mid circumferential plane 107.
  • a strut 196 for tensioning the belt 36 connects the axle 60 at the adjustment pin 188 to a foundation member-198.
  • the adjusting apparatus 194 includes a screw bolt 200 which threadably joins the axle adjustment region 192 to the strut 196.
  • a pair of hydraulic cylinders 202 each have a rod end 204 and a head end 206 which are respectively connected to the foundation member 198 and a thrust block 208 which is lon itudinally slideable on the foundation member 198.
  • a retainer 210 is positioned vertically adjacent the thrust block 208, extends laterally adjacent the foundation member 198, and is joined to the thrust block 208 by a screw bolt 212.
  • Four retainer/screw bolt combinations 210,212, one above and one below at each lateral end of the thrust block 208, are utilized with the present invention.
  • the thrust block 208 is pivotally mounted on the frame 18 by a swivel pin 214 which is coaxial with the pivot pin axis 182.
  • the alignment members 84 sequentially pass through an alignment phase and a load carrying phase during their residence or partial residence in the wheel structures' guide channels 46,48 and the roller structures' guide slot 174.
  • the alignment phase begins when the inner locating surface portions 140 of the alignment members and the base positioning surface portions 50,52 move into lateral adjacent relationship. Lateral alignment of the wheel or roller structures and the alignment members 84 is provided by the progressive entry of the alignment members 84 into the guide channels 46,48 and guide slot 174. If misaligned, the appropriate base positioning surface portion 50,52 serially engages the adjacent inner 140 and base 138 positioning surface portions to initially induce lateral deformation of the alignment members 84 which deformation decreases with increasing entry to cause relative lateral displacement of the alignment members 84 and the wheel or roller structures.
  • the load carrying phase begins upon complete entry of the alignment members 84 in the guide channels 46,48 and slot 174 and continues until alignment members 84 exit therefrom. Discussion herein of the guide structure 82*s interaction with the wheel and roller structures is limited to the load carrying phase of engagement therebetween.
  • Figs. 12A, 12B, and 12C illustrate cross-sectional views of the relative configuration of the preferred driver wheel structure 85 and the entraining belt 36 for increasing degrees of side force exerted by the wheel structure 85 on the belt 36.
  • Fig. 12A illustrates the engaged wheel structure and entraining belt for linear movement of the vehicle 10 on terrain having no side slope. There is a running clearance at the outer periphery 32 of the wheel structure 85 between laterally adjacent locating 134 and positioning 50,52 surfaces of approximately .3 centimeters.
  • Fig. 12B illustrates the belt/entrained drive wheel structure 85 when the vehicle 10 is operated on a side slope or is making a turn.
  • the respective base portions 138 and 96 of the guide structure's left locating surface and the wheel structure's right positioning surface 50 deform to provide surface engagement therebetween.
  • the deformation illustrated in Fig. 12B is characteristic for most side hill conditions or vehicle turns and constitutes a radial distance * of engagement therebetween of approximately 2 1/2% of the wheel's diameter.
  • Fig. 12C illustrates the belt/entrained driver wheel structure 85 when the utilizing vehicle 10 is making a turn on a steep side slope.
  • the base portions 138,96 of adjacent left locating and right positioning surfaces have fully engaged but such surface engagement remains near the wheel structures' outer periphery since the lateral engagement area therebetween is within 5% of the wheel structures' outer periphery.
  • FIG. 13 is a graphical representation of the lateral loads which are supported by the guide structure 82 as a function of the guide structure's deformation. Numbers have not been placed on Fig. 13 because the load and deformation magnitudes are a function of the vehicle weight, the material characteristics of the drive wheel and entraining belt, and the relative size of the engageable positioning and locating surfaces. Fig. 13 is instructive, however, for purposes of noting the trend in guide structure/driver wheel deformation for increasing load.
  • the configuration of Fig. 12A operates in the region designated 12A on Fig. 13 where there is no load and no deformation.
  • the configuration illustrated in Fig. 12B operates at the point designated 12B on Fig. 13 where some limited locating surface/positioning surface deformation has been sustained in resisting the side load.
  • the belt/driver wheel configuration illustrated in Fig. 12C occurs for the deflection and load indicated on Fig. 13 by the reference numeral 12C.
  • the base portions of the elastomeric .locating 134 and positioning 50 surfaces have become completely engaged and an more load exerted thereon will be resisted at a higher rate and lower deformation since the location surface's inner portion 140 will thereafter increasingly engage the inner portion 98 of the rigid drum's positioning surface 50.
  • Such increased load acceptance for a given deformation is graphically represented by the relatively steeper slope on the load/deformation curve of Fig. 13 for loads and deformations greater than those corresponding to the point marked 12C.
  • Maintaining the friction couple between the driver wheel structures and associated belts minimizes the relative motion and reduces wear thereof. Insofar as engagement therebetween is limited to the radially facing driver wheel and belt surfaces, the wear problem does not exist. Maintaining lateral registry of the driver wheel 44 and belt 36 when lateral loads are exerted on either necessitates engagement between lateral surfaces of both. Such lateral surface engagement results in relative motion between the wheel and belt at the points on the wheel where the belt initially engages and disengages therewith. Between such points the lateral engaging surfaces either have no relative motion or are not engaged. At such points, however, the belt is moving in a linear mode while the mating wheel is rotating and relative motion between the laterally engaging surfaces is unavoidable. Increasing relative motion results at increasing radial
  • the belt's alignment members 84 are laterally tapered in a convergent manner such that their locating surfaces 134 diverge from the adjacent positioning surfaces 50,52 to minimize the lateral surface contact therebetween but are not tapered to such an extent that the driver wheel 44 can easily "walk up" the side thereof and unbelt itself.
  • Multiple alignment members 84 are used rather than a continuous member to avoid the elevated levels of compression on the innermost fibers thereof during belt conformance around the entrained wheel structures.
  • the lateral most passes of the belt's longitudinal filament is) 142 are arranged laterally beyond the driver wheel's outer peripheral surface 32 with which the belt is engaged as illustrated in Figs. 12A, 12B, and 12C.
  • the purpose of such disposition is to lower the stresses imposed on those laterally outermost filaments when extreme amounts of debris are ingested between the belt 36 and wheels 24,26.
  • Such outer filaments experience the highest stress levels because ingested debris typically has a wedge shaped cross section with the greatest thickness being at the lateral extremes of the belt 36.
  • the driver wheel 44 is laterally tapered at its outer periphery 32, but an equally effective solution ' to such problem is to laterally extend the belt and longitudinal filaments beyond the lateral edges of untapered driver wheel structures. Both such arrangements contribute toward the goal of accommodating debris ingestion without damaging propulsion system components.
  • Fig. 15 illustrates the projected relative mean efficiencies of 4-wheel drive agricultural tractors and the present invention belted vehicle 10 in four different soils/soil conditions.
  • Efficiency is defined as the ratio (expressed as a percentage) of the vehicle's drawbar horsepower divided by engine horsepower.
  • Mean efficiency is the average of the vehicle's peak efficiency and the efficiency corresponding to a pulling force 10% less than that exerted at the peak efficiency. Such mean- efficiency is considered representative of the actual way an agricultural tractor is used. While it is to be understood that soils and their conditions constitute a continuum based on many factors such as moisture, ground compaction, etc.
  • the firm, strong classification is generally represented by Midwest soil, refers to the soil's high resistance to vehicular sinking and high shear strength, and constitutes about 35% of the U.S. acres presently tilled by 4-wheel drive vehicles.
  • the firm, weak classification generally represents Southwest soil, refers to the soil's high resistance to vehicular sinking and low shear strength and constitutes about 30% of the U.S. acres now tilled with 4-wheel drive vehicles.
  • the tilled classification is generally representative of any farmed soil which has already been plowed or otherwise tilled and constitutes about 25% of the 4-wheel drive-tilled acres in the U.S.
  • the soft, weak classification is generally represented by any soil which is wet and loose, refers to the soil's low resistance to vehicular sinking and low shear strength, and makes up about 10% of the acres presently tilled in the U.S. by 4-wheel drive vehicles.
  • the belted vehicle's advantage varies from 8.0% in firm, strong soil to 56% in soft, weak soil. In general, the softer and looser the soil, the greater will be the belted vehicle's advantage.
  • Propulsion system "slip percentage” is defined as the following ratio expressed as a percentage: 100- [ (velocity of the vehicle) /(velocity of the propulsion system's ground engaging portion)] .
  • the maximum pull/weight ratio of 4-wheel drive vehicles varies with soil conditions, vehicle balance, load characteristic, etc., but generally corresponds to a slip percentage averaging about 20-40%, as compared to the belted vehicle, whose maximum pull/weight ratio generally corresponds to a slip percentage of about 8-15%.
  • Fig. 16 diagrammatically illustrates a representative set of curves which show the belted vehicle developing its maximum pull/weight ratio at a substantially lower slip percentage than does the
  • the belted and 4-wheel drive tractors exerted approximate respective ground pressures of 3.45 Newtons per square centimeter and 10.3 Newtons per square centimeter. While it is well-known that crops often grow faster in soils having little compaction as compared to soils having greater compaction, one agriculturist actually observed that crops grown in soil tilled by the belted vehicle grew faster than crops grown in soil tilled by the higher powered, heavier 4-wheel drive tractor.
  • Vehicle operators reported a smoother ride from the belted vehicle 10 as compared to the wheel tractor which improvement manifests itself in comparatively improved operator performance as the time of operation increases.
  • the ride improvement is also indicative of reduced maintenance requirements of chassis mounted components since those components are isolated from impact loads which commonly occur in traversing uneven terrain.
  • an elastomeric belt laying vehicle 10 which traverses improved road surfaces at high speed without inflicting damage, which has superior tractive effort and low unit ground pressure as compared with comparably powered wheel vehicles, and which provides improved ride characteristics as compared with wheeled vehicles used in comparable conditions.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Transportation (AREA)
  • Mechanical Engineering (AREA)
  • Tires In General (AREA)
  • Harvesting Machines For Specific Crops (AREA)
  • Belt Conveyors (AREA)
  • Sowing (AREA)

Abstract

Véhicule à courroie élastomère (10) pour transmettre un effort de traction à la terre supérieur à celui des véhicules à roues à entraînement comparable et pouvant fonctionner à vitesse élevée sur des surfaces de route améliorées sans leur infliger d'endommagement. Une paire de roues (24, 26) est disposée de chaque côté latéral (28, 30) du châssis (12) du véhicule pour soutenir ce dernier. Une courroie sans fin inextensible (36) est tendue fortement sur toute sa longueur entraînée autour de chaque paire de roues (24, 26) et couplée par friction de manière motrice à au moins une roue (24) de chaque paire. La structure de la courroie (36), la structure des roues (24, 26) et les composants de coopération (46, 48, 82) assurent un engagement entre ces différentes pièces, permettent une longue utilisation avec un entretien minimum et fournissent le couple de friction nécessaire pour transmettre de façon efficace le couple d'entraînement des roues (24) à la courroie (36).
PCT/US1984/000560 1983-12-20 1984-04-10 Vehicule de travail a courroie a entrainement par friction WO1985002824A1 (fr)

Priority Applications (3)

Application Number Priority Date Filing Date Title
DE8484901712T DE3479019D1 (en) 1983-12-20 1984-04-10 Frictionally driven belted work vehicle
BR8407219A BR8407219A (pt) 1983-12-20 1984-04-10 Veiculo de trabalho de assentamento por correia
CA000468799A CA1222271A (fr) 1983-12-20 1984-11-28 Vehicule de travail a courroie - chenille souple de traction

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US56333883A 1983-12-20 1983-12-20
US563,338 1983-12-20

Publications (1)

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WO1985002824A1 true WO1985002824A1 (fr) 1985-07-04

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EP (2) EP0165245B1 (fr)
JP (1) JPS61500720A (fr)
AU (1) AU578024B2 (fr)
BR (1) BR8407219A (fr)
DE (2) DE3479019D1 (fr)
IT (2) IT8454198V0 (fr)
MX (1) MX161717A (fr)
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WO (1) WO1985002824A1 (fr)

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Also Published As

Publication number Publication date
USRE37174E1 (en) 2001-05-15
AU578024B2 (en) 1988-10-13
EP0165245B1 (fr) 1989-07-19
DE3479019D1 (en) 1989-08-24
US5279378A (en) 1994-01-18
DE3486066D1 (de) 1993-03-18
JPS61500720A (ja) 1986-04-17
DE3486066T2 (de) 1993-08-19
MY100905A (en) 1991-05-16
EP0165245A1 (fr) 1985-12-27
BR8407219A (pt) 1985-11-26
EP0305647A1 (fr) 1989-03-08
AU2860184A (en) 1985-07-12
IT1179880B (it) 1987-09-16
MX161717A (es) 1990-12-18
IT8468261A0 (it) 1984-12-19
IT8454198V0 (it) 1984-12-19
EP0305647B1 (fr) 1993-02-03
JPH059315B2 (fr) 1993-02-04

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